Vibratory pump



Feb. 12, 1963 G. BANERIAN 3,077,162

VIBRATORY PUMP Filed May 24, 1956 4 Sheets-Sheet 1 IN V EN TOR. GORDON BANE RIAN JMQ? ATTORIV X G. BANERIAN VIBRATORY PUMP Feb. 12, 1963 4 Sheets-Sheet 2 Filed May 24, 1956 INVENTOR. GORDON BA/VER/A/V INTO/75 4 Sheets-Sheet 4 INVENTOR. GORDON BA/VER/AN M Q TTOR EY.

Feb. 12, 1963 G. BANERIAN VIBRATORY PUMP Filed May 24, 1956 du n Ohio Filed May 24, 1956, Ser. No. 587,096 2 Claims. (Cl. 103-159) This invention relates to pumps and more particularly to shaftless vibratory liquid pumps having no seals. An object of the invention is to provide a pump that is adaptable for use in the nuclear and chemical fields in that there are no moving parts or seals that can leak to the exterior.

The nuclear and chemical fields have developed a need for a pumping mechanism for use in installations where fluids are pumped to high pressures. Further, the fluids used are of a type that no known sealing mechanism will withstand without leaking. It is imperative that fluid leakage be completely eliminated because of the danger in handling radioactive, toxic, corrosive or inflammable fluids.

The shaftless vibratory pump of the present invention is a double acting displacement pump consisting of a cylinder, piston and-inlet and outlet valves. This pump dif- Ife'rs firom conventional pumps in that there are no seals "-andno shaft or connecting rod attached to the piston. To accomplish the pumping action the cylinder is vibrated along its axis producing a relative motion between the cylinder and free floating high inertia piston.

One embodiment of the present invention is that the mass of fluid contained in the cylinder is used in place of the piston. Also, a rotor reciprocated about a completely enclosed free floating stator accomplishes the necessary relative movement between the parts and creates the fluid pumping action.

By using the inertia properties of the free floating piston,

' the mass of fluid as a pumping means or the reciprocating rotor about the stator, the desired pumping of dangerous fluids to ahigh pressure is permitted with relatively simple mechanical parts. Actually, the only additional fluid control means are inlet and outlet check valves which can be of the conventional reed type and which may be eliminat'ed iflow efiiciency can be tolerated or orifices with high reverse flow loss coefficients can be used in place of the check valves.

The foregoing and other features of the invention will be better understood from the following description taken in connection with the accompanying drawings of which:

FIG. 1 is a section of the pump on the line 1-1 of FIG. 2;

FIG. 2 is a section on the line 22 of FIG. 1;

FIG. 3 is a section on the line 3-3 of FIG. 4, which is a modification of the pump shown in FIG. 1;

FIG. 4 is a section on the line 4-4 of FIG. 3;

FIG. 5 is a section of a series of pumps arranged in series order;

FIG. 6 is a section of a series of pumps arranged in parallel order;

FIG. 7 is a section on the line 77 of FIG. 9;

FIG. 8 is a fragmentary section on the line 88 of FIG. 7; and

FIG. 9 is a section on the line 9-4! of FIG. 7.

Referring to the drawings the simplest disclosure of my device is in FIGS. 1 and 2. A pump cylinder 10 cylindrical in fiorm, except for the longitudinal ridges 11 and 12, is constructed in a leakproof manner. Pump chamber 13 has slidably disposed therein a free floating high inertia piston 14. Lubrication means for the piston 14 resides or lug 15 attached to or forming a part of the rear end of pump cylinder in has pivotally secured thereto at 16 a connecting rod 17 which is reciprocated by means of the conventional crank 18 and pin 19. Vibratory movement is thus imparted to pump cylinder 10 along its axis to produce relative movement between same and the high inertia piston therein. Any Well known mechanism might just as well be employed for imparting the vibratory movement to accomplish the pumping action. The only openings into the shaftless pump cylinder 10 are the liquid inlet and outlet conduits. Orifice 2%} in longitudinal ridge 11 receives the inlet tubing 21 which is spiraled about the pump cylinder in the manner clearly shown in FIGS. 1 and 2 of the drawings. This spiraling of the liquid inlet tubing permits the necessary flexing action which accompanies the rapid vibratory movement of the pump cylinder induced by its actuating mechanism. Orifice 22 in longitudinal ridge 12 has secured therein liquid outlet tubing 23, which is spiraled about the pump cylinder 10 in a manner similar to tubing 21 to permit flexing thereof and insuring against fracture at the pump cylinder and liquid supply connections. Obviously other means of disposing or bending the liquid inlet and outlet tubes might well be employed as long as the necessary flexing: thereof is permitted.

The interior ofi longitudinal ridge 11 is drilled to form passage 24 connecting the liquid inlet orifice 20 with'the front inner end of pump chamber 13 through chamber inlet orifice 25. A second pump chamberinlet orifice 26 3 at the other end of apertured ridge 11 permits liquid flow into the rear inner endof pump chamber 13. Check valve 27 on seat or orifice 25 controls the flow of liquid in a single direction, namely, into the front end. of pump chamber 13. Check valve 28 similarly controls the flow of fluid into the rear end of pump chamber 13. r

The interior of longitudinal ridge 12 is also opened a 29 to the outgoing liquid and similarly communicates with the front end of the pump chamber by means of orifice 3i) and at the rear end by orifice 31. These pump chambers communicating liquid orifices are check valved at 32 and 33 to permit liquid flow in a single direction, namely outward.

FIGS. 1 and 3 are essentially the same and the same numerals have been used in FIGS. 1 to 4. In FIGS. 3 and 4, the high inertia piston 14- has been omitted, and it is intended that the mass of liquid in the pump chamber will largely compensate for the heavy free floating piston. The high inertia piston 14 and/ or the mass of liquid in pump chamber 13, upon rapid vibratory action of the pump cylinder 10, tend to maintain a stationary position, and thus creates a relative movement between the cylinder and piston upon a longitudinal axis that furnishes the double acting displacement type liquid pumping action. Reciprocation in one direction induces liquid flow through the check valves into the low pressure side of the piston, and simultaneously discharges compressed liquid from the high pressure side of the piston through the check valves controlling the outflow orifices. There are no seals, gaskets or leak proofing mechanism other than those required to form the pump chamber. The pump obviously is selfi-lubricating and there are no moving parts to create friction.

FIGS. 5 and 6 illustrate the use of a number of the inertia pumps of my invention. FIG. 5 shows a series arrangement of four pumps. FIG. 6 shows four pumps in parallel arrangement. It will be appreciated that a greater or lesser number of pumps can be used in either combination. When the pumps are used in series combination, higher pressure is obtained while the displace ment remains the same as for an individual pump. In parallel combination, as shown in FIG. 6, the overall displacement is increascd while the pressure remains the same as for an individual pump. The parallel arrangement has the advantage of requiring substantially fewer check valves than other arrangements, which also effects a considerable savings in cost.

In FIG. 5, the series of pump chambers are adapted to be actuated by a mechanism either the same or similar to that shown in FIG. 1. Inasmuch as the multiple pumps are actuated as a unit, the only flexibility required in the liquid lines is that shown at 34, namely, coiling of the liquid inlet tube 36 and coiling 37 of the liquid outlet tube 38. Liquid inlet tube 36 provides dual liquid inlets 39 and 40 into the front end 41 and the rear end 42, respectively, of pump cylinder 10. Front liquid inlet 39 is check valved at 43 and rear liquid inlet 40 is check valved at 44. A check valve 45 in liquid outlet tube or conduit 46 connects the rear end 42 of the first cylinder with the front end 47 of second adjacent pump 10a. Check valve 48 in outlet tube 49 connects with the front end 41 of the first pump with the rear end 50 of second pump 10a. Second pump 10a is connected to adjacent third pump 10b by means of check valve 51 in liquid outlet tube 52. This permits liquid flow from the rear end 50 of pump 10a to the front end 53 of pump 10b. Liquid flow from the front end 47 of pump 10a to the rear end 54 of pump 10b is accomplished through check valve 55 in short conduit 56. Liquid is pumped from the rear end 54 of pump 10b to the front end 57 of fourth pump 10c through check valve 58 in tube 59. Liquid flow from the front end 53 of pump 10b to the rear end 60 of pump 10c is pumped through check valve 61 in outlet tube 62. Fluid in rear end 60 is pumped through check valve 63 in conduit 64 and thence into the main conduit 38. The fluid in front end 57 is pumped through check valve 65 in conduit 66 and thence into the main conduit 38.

The modification of my invention shown in FIG. 6 is nothing more than a parallel arrangement of the same shaftless vibratory pump. The pump cylinder 10 and its floatable high inertia piston 14 of FIG. 6 are vibrated by suitable mechanism heretofore described. The parallel pumping unit has a liquid inlet tube 67 coiled at 68 for flexibility. The liquid outlet conduit 69 for the multiple pumps also has flexible coils 70 for the same purpose. In this arrangement, the liquid conduit 67 is bifurcated at 71 and the dual parallel liquid inlet pipes 72 and 73 are check valved at 74 and 75, respectively. Pump 10 has liquid inlets from the main parallel tubes entering the rear of the pump at 76 and at the front at 77. Similar inlet members '78 and 79 enter the rear end 80 and the front end 81 of pump 10a. Also, conduits 82 and 33 provide liquid admission to the rear and front ends of shaftless vibratory pump 10b. The ends of the main inlet fuel tubes enter the rear of the multiple pump 10c at 84 and the front at 85.

Dual liquid outlet conduits 86 and 87 relieve pump 10 t at the rear and front by means of conduits 88 and 89. Vibratory pump 10a has tubes 90 and 91 providing liquid outlets from the rear and front thereof. Tubes 92 and 93 from the rear and front of multiple pump 10b empty into the main liquid outlet. Finally, the conduits 94 and 95', respectively, from the rear and front of pump 10c empty into the parallel liquid tubes 86 and 87. Check valves 96 and 97 adjacent the bifurcated section 98 of the outlet tube 69 control the liquid exit from the multiple pumping system. Displacement of the liquid by the double action pumping movement created by the free floating high inertia piston and the vibrated cylinder induces continuous liquid flow into each pump simultaneously rather than progressively as shown in FIG. 5, and the discharge from the multiple pumps is also simultaneous into the dual parallel outlet conduits controlled by the check valves in the bifurcated section thereof.

Referring now to FIGS. 7, 8 and 9 of the drawings, there is shown a somewhat different arrangement of shaftless vibratory pump parts, but which nevertheless opit erate on the same principle of pumping. In this instance, the stator 99 is equivalent to the free floating high inertia piston of PEG. 1 and acts in substantially the same manner. The leakproof rotori1tl0 completely surrounding the stator is so constructed as to render any leakage of liquid from the pump practically negligible. The rotor can be formed of two interfltting parts 101 and 102 which are connected by a leakproof method of construction. The vibratory action of the cylinder 10 has been changed to an oscillating movement of the rotor which creates relative motion between the rotor and stator similar to the relative motion between the cylindrical pump 10 and its piston whether solid or a mass of liquid. The rotor 100 has a plurality of protuberances 101a extending radially inwardly, and has multiple fluid pump chambers 103 formed therein which are engaged by the small free floating high inertia piston like heads or projections 104. Oscillation of the rotor about the stator creates a double action liquid displacement pumping action similar to that heretofore described. Means for injecting the liquid into the multiple pump chambers is provided first by a spiraled inlet tube 105 which, because of its flexible mounting, may easily withstand the oscillatory action of the pump without fracture. Tube 105 delivers to a liquid inlet 106 disposed centrally of rotor plate 101. From inlet 106, liquid supply tubing 107 radiates therefrom, same being formed in the plate as clearly shown in FIG. 7. Tubes 107 are bifurcated adjacent their delivery ends 108 and 109, respectively, and each bifurcattion is check valved at 110 and 111 to control the liquid inlet flow. Bifurcation 108 delivers into one side of one of the multiple pump chambers, and the other bifurcation 109 delivers into the opposite side of adjacent pump chamber.

The liquid outlet system is almost identical, and bifurcated liquid outlet tubes 112 and 113 relieve alternate pump chambers past outlet check valves 114 and 115 in said bifurcated tubes respectively. Radially disposed outlet conduits 116 formed in rotor plate 102 deliver centrally at 117 to flexible spiraled outlet tube 118. Any means for oscillating the vibratory pump may be provided and may assume the shape as shown in FIG. 9, such as a spider welded to the rotor plate 101 and extending outwardly. A shaft 131 is fixedly attached to the spider 130. A similar spider 132 and shaft 133 are attached to the rotor plate 102. In the lower portion of the rotor plate 101 as shown in FIG. 7, a movable link 136 is rotatably attached to the pin that in turn is fixedly attached to the rotor plate 101. The eccentric 137 has a pin 138 fixedly attached thereon to which the movable link 136 is connected. An electric motor (not shown) may be attached to the central pin 139 of the eccentric 137 to rotate the eccentric at a uniform speed. In conventional manner the eccentric and link arrangement on the reciprocatory pump will cause the pump to oscillate at a uniform rate.

The only difference in the modifications of FIGS. 7, 8 and 9 and the other figures is in the actual makeup of the simple parts, and the device operates upon the same principle and in essentially the same manner.

Essentially, although requiring a most detailed explanation to describe the mechanical elements, their arrangement and advantages, there is shown a relatively simple, vibrated, oscillated or reciprocated pump having a relative motion transmitting action with respect to its free floating high inertia piston that produces a positive high pressure pumping action. This is a much desired and needed device, in view of the fact that the pump is selflubricating, completely without seals and devoid of actuating shafts.

The mechanism is simple and lends itself to other highly desirable construction accomplishing exactly the same results, but it is believed that the detail of disclosure and description herein is entirely suflicient to support the claimed invention as indicated by the supporting claims.

I claim:

1. A pump comprising: a housing, a cylindrical stator rotatably received by the said housing, a plurality of pro jections extending radially outwardly from said stator, a plurality of protuberances extending radially inwardly from said housing and positioned between and in spaced relation to said stator projections, said housing having a plurality of inlets and outlets positioned between said projections and protuberances, a plurality of check valves received by said housing inlets and outlets, a first conduit means interconnected to said housing inlets, a second conduit means interconnected to said housing outlets, and a means for oscillating the housing for causing a double acting displacement pumping action.

2. A pump comprising: a housing, a cylindrical stator rotatahly received by the said housing, a plurality of toothlike projections extending radially outwardly on said stator being in spaced relation from each other, said housing having a plurality of slots therein each receiving one or more stator projections, said projections having a length shorter than the length of said slots, said projections being in sealing engagement with the said housing slots, said housing having a plurality of inlets and outlets positioned between said projections and said housing slots, a plurality of check valves received by said housing inlets and outlets,

a first conduit means interconnected to said housing inlets, a second conduit means interconnected to said housing outlets, and a means for operating the housing for causing a double acting displacement pumping action.

References Cited in the file of this patent UNITED STATES PATENTS 67,580 Poston Aug. 6, 1867 391,189 Pontallie Oct. 16, 1888 711,128 Schirmer Oct. 14, 1902 915,744 Costephens et al Mar. 23, 1909 1,831,993 Braselton et al Nov. 17, 1931 1,955,992 West Apr. 24, 1934 2,019,023 Seilliere Oct. 29, 1935 2,282,597 Archer May 12, 1942 2,814,551 Broeze et a1 Nov. 26, 1957 2,839,237 Dolz June 17, 1958 FOREIGN PATENTS 3,206 Austria of 1901 84,759 Norway Oct. 23, 1954 274,278 Germany May 18, 1914 

1. A PUMP COMPRISING: A HOUSING, A CYLINDRICAL STATOR ROTATABLY RECEIVED BY THE SAID HOUSING, A PLURALITY OF PROJECTIONS EXTENDING RADIALLY OUTWARDLY FROM SAID STATOR, A PLURALITY OF PROTUBERANCES EXTENDING RADIALLY INWARDLY FROM SAID HOUSING AND POSITIONED BETWEEN AND IN SPACED RELATION TO SAID STATOR PROJECTIONS, SAID HOUSING HAVING A PLURALITY OF INLETS AND OUTLETS POSITIONED BETWEEN SAID PROJECTIONS AND PROTUBERANCES, A PLURALITY OF CHECK VALVES RECEIVED BY SAID HOUSING INLETS AND OUTLETS, A FIRST CONDUIT MEANS INTERCONNECTED TO SAID HOUSING INLETS, A SECOND CONDUIT MEANS INTERCONNECTED TO SAID HOUSING OUTLETS, AND A MEANS FOR OSCILLATING THE HOUSING FOR CAUSING A DOUBLE ACTING DISPLACEMENT PUMPING ACTION. 